Pump



Jan. 21, 1936. A.' F. SHERZER PUMP Filed July 3,

3 Sheets-Sheet 1 m M a d ATTORNEY s jam. 21, 1936. A. F. SHERZER 2,928,569

PUMP

Filed July 3, 1933 3 Sheets-Sheet 2 INVENTOR ATTORNELS Jan. 21, 1936. A, F, SHERZER 2,028,569

PUMP

Filed July 3, 1933 3 Sheets-Sheet 5 INVENTOR flZZenZSZerZer ATTORNEYS atented Jan. 21,

UNITED STATES PATENT OFFICE 13 Claims.

The invention relates to pumps and has for one of its objects to provide a pump which is simple in construction and relatively cheap to manufacture. Another object is to provide a pump which is relatively efi'icient in operation and which discharges the liquid pumped thereby into 'a gaseous medium and more particularly the atmosphere. Other objects are to provide a pump which for a given discharge and lift requires relatively low power for its operation; to provide means for reducing the interference between the rotating arms and the liquid discharged from them; and to provide and prescribe proportions of the parts of the pump to secure satisfactory operation.

These and other objects of the invention will become apparent from the following description, taken in connection with the accompanying drawings, in which Figure l is a diagrammatic sectional view illustrating an embodiment of my invention;

Figure 2 is a similar view, illustrating another embodiment of my invention;

Figure 3 is a plan view illustrating another embodiment of my invention;

Figure 4 is an elevation, Figure 3;

Figures 5 and 6 are views similar to Figures 3 and 4 respectively, and illustrating another embodiment of my invention;

igure 7 is a diagrammatic sectional view illustrating another embodiment of my invention;

Figure 8 is a cross section on the line 8-8 of Figure 7;

Figure 9 is a cross section of Figure 8;

Figure 10 is a plan view illustrating another embodiment of my invention;

Figure 11 is an elevation thereof;

Figures 12, 13, and 14 are sectional elevations illustrating other embodiments of my invention.

In general, the field of application of the pump embodying my invention is limited to heads up to about 30 feet for cold water or less if the water is warm, but it is understood that the pump may be used for pumping fluids other than water, in which case there may be other limitations of the head. The pump comprises a rotatable vessel capable of containing a fluid and having a fluid inlet and a fluid outlet. The fluid is discharged from the outlet into a gaseous medium, preferably the atmosphere. Suitable means for driving the pump may be used. The present application is a continuation in part of my application Serial No. 551,764 filed Septempartly in section, of

on the line 99 her 8, 1931 and now abandoned and also my copending application Serial No. 636,061 filed October 3rd, 1932, and this present application is directed to and claims the generic subject matter.

Referring to Figure 1, the vessel comprises the inlet chamber I and the radiating arm 2, both of which rotate in the atmosphere about the fixed center or axis 0. The arm has in its outer end the discharge outlet or orifice 3. The vessel is. filled with fluid, such as water, and provision is made for a constant supply of the water at a pressure, such as atmospheric pressure, at the center or axis 0. The orifice 3 has the area A square feet and the coefiicient of discharge K and the distance from the center of the orifice to the center or axis 0, or the radial length of the arm 2, is r in feet. The arm is so curved with respect to the direction of rotation as to discharge the liquid rearwardly in a direction of substantially degrees to the peripheral speed vector at the center of the orifice.

If the vessel is rotated about the center or axis 0, with the angular velocity w, a pressure head is built up owing to centrifugal force of substantially 2!? where V=wr. Liquid flows through the orifice 3 under this head produced by rotation with a relative velocity W in feet per second which is, if losses be neglected, always equal to the peripheral velocity V in feet per second. It is important to remember that the relative velocity W is always equal to the peripheral velocity V, neglecting losses. In practice, a close approximation to this may be secured. The quantity of water discharged from the vessel may be computed from the simple equation for the fiow from any orifice.

If under conditions assumed in Figure 1, the liquid is supplied at the center or axis 0, under atmospheric pressure and discharges through the orifice 3 into the atmosphere, the vectors of peripheral speed V and relative velocity W would theoretically be equal and opposite and the absolute velocity C would be zero. This means as well that, neglecting mechanical and hydraulic losses, little, if any, power would be required to rotate the vessel. At first glance, it may be hard to see how the power can be zero if liquid is discharged. This is owing to the fact that the vessel is in effect a close combination of a cenc5 trifugal pump and a reaction turbine in series. Neglecting hydraulic and mechanical losses, all the work done on the water in the centrifugal pump element is regained in the reaction turbine element and the net result is zero power expenditure. This is true if the pressures at the inlet and the outlet are equal.

It is desirable that the liquid be discharged substantially tangent to a circle passing through the center of the discharge orifice 3. This means that the face of the discharge orifice lies substantially in a radial plane. In the discharge of liquid through an orifice there is generally a certain contraction of the stream lines which causes the issuing jet to be somewhat smaller in cross section than the orifice from which it was discharged. The minimum cross section of the jet is known as the vena'contracta. It is at this point that the maximum velocity of discharge W occurs. The vena contracta is usually located slightly down stream from the face of the orifice, the amount depend ing on the design of the orifice. To secure best results, the center of the vena contracta 4 should be substantially in a radial plane. Slight departures of a few degrees from this are not serious, but it is better to have it as near as possible to the radial plane.

If the vessel is arranged, as shown diagrammatically in Figure 2, and embodying the arrangement shown in Figure 1, a very useful and eificient pump is produced. Referring particularly to Figure 2, the vessel comprises the central inlet-chamber 5 and the diametrically opposite arms 6 and is rotated in a horizontal plane about the vertical fixed center or axis l. The vertical pipe 8 extends axially down from the center of the vessel to the body 9 of the water to be pumped and having the level 10. This pipe may rotate with the vessel and is provided with the check valve II at its lower end. The arms have the discharge: outlets or orifices l2 which open oppositely to each other and proride for the discharge of the water at an angle B substantially of 180 degrees or in a direction opposite to the direction of rotation. These orifices are preferably located so that the vena contracta of each is substantially in a radial plane. Atmospheric pressure acts upon the level of the body of water 9 and the orifices l2 are open to the atmosphere.

Assuming the vessel comprising the inlet chamber 5, the arms 8 and the pipe 8 to be initially filled with water before being set in rotation by the electric motor 13, which is above and suitably connected to the vessel, it will be seen that when the vessel is set into rotation the water will fiow out of thedischarge orifices at the tips of the arms, thereby creating a partial vacuum at the center of the vessel. Because of this vacuum, the atmospheric pressure will force more water into the pipe 8 and up to the vessel, where it is continually discharged by action of centrifugal force. Since the water is discharged from the arms in a direction opposite to that of rotation of the vessel, the relative and peripheral velocities'are nearly equal and opposite and the absolute velocity is low, this being determined by the static head and hydraulic losses. This means that the water will fall nearly vertically downwardly, so that it will drop into a suitable container, such as the annular container |4,-below the vessel and having the discharge outlet M3. The water has then been lifted througha height equal to the distance between the water level I and the; plane of rotation of the arms 6, or, more particularly, the discharge orifices l2 and the pump for doing this may be called a centrifugal reaction pump.

An analysis of the vector relations for a typical case is as follows: Assume the arms to rotate with a peripheral velocity V at the orifices of 150 feet per second and that the vacuum produced at the junction of the rotating arms and the vertical pipe is 20 feet. The head producing fiow through the orifices may be computed from the well-known formula feet Neglecting hydraulic losses and the static head, the water would discharge from the orifices with a relative velocity W of 150 feet per second produced by the above head of 351 feet, if the pressure at the center were that of the atmosphere and the orifices were open to the atmosphere. Since a vacuum of 20 feet has been assumed at the center, the relative velocity W will be that caused by the head 35120 feet or 331 feet. The velocity due to this head of 331 feet is V=1/64.4X331=146 feet The absolute velocity C will be the difference 150146 4 feet per second in the direction of rotation. This is a leaving loss which can never be eliminated, but which may be made small by using a relatively high tip or peripheral speed V. The mechanical losses in such a pump may be kept low, since the vessel rotates in the atmosphere and nearly all the power applied to the vessel is usefully spent in raising the water. This will make possible unusually high efficiency.

In the application of the principles of my invention to practice, certain proportions of the elements are of great importance. In order to have satisfactory operation, it is necessary to proportion the area of the discharge outlet or orifice according to the area of the central inlet chamber or the area of the centralinlet or supply pipe, whichever is the smaller. It is also necessary to proportion these areas according to peripheral speed of the vessel at the center of the discharge outlet or orifice. The maximum area at the discharge outlet or orifice or the maximum aggregate area at the discharge outlets or orifices, if more than one is used,'should not exceed the value given by the formula where'Az is the area of the discharge outlet or orifice or the aggregate areas of the discharge outlets or orifices, V, is the peripheral velocity in feet per second of the vessel measured at the center of the discharge outlet or orifice and A is the cross sectional areaof the inlet chamber or inlet pipe, whichever is the smaller, the areas A2 and As being in square feet.

The area A2 must not exceed that given'by'the above formula if the pump is operating as a suction lift with cold water and at standard barometric pressure at sea level. With a positive pressure head existing in the central supply chamber the area A2 may be increased, although this is not recommended, since smaller values of A; will yield better results.

In order to obtain reasonable values of efficiency, the diameter of the inlet chamber to which the outlet arms are connected should -bear some relation to the rotative speed. This result may be expressed by the following equation:

where Dr is the diameter in feet of the inlet chamber. Smaller values of D1 will be found to be more efiicient, but the value should not exceed that given by the above formula.

All of the pumps embodying my invention and including those illustrated embody the above proportions.

Also in the application of the principles of my invention to the actual construction of centrifugal reaction pumps certain very definite problems present themselves. Of these the most evident is that of the interference between the water discharged from one orifice and the following arm. Assume the axes of all orifices to lie in a horizontal plane. The water discharged has therefore no downward component to its velocity and must depend on gravity to get it below the level of the next following arm. This falling of the water below the lowest level of the next following arm requires the elapse of a certain interval of time and it may happen that if the rotative speed is too high the Water will not have time to fall far enough to clear the following arm and considerable objectionable splashing and consequent waste of power will result. This suggests a certain classification of centrifugal reaction pumps into (a) Low speed pumps.

(1)) High speed pumps.

A low speed pump would therefore be one in which the water had sufiicient time to fall clear of the revolving arms between the passage of successive arms past a given point. The greater the number of arms, the shorter will be the allowable time interval for falling and the lower must be the rotative speed to avoid interference. This interference may be noted even in the extreme case of a pump with but one arm, but the rotative speed at which it occurs will be higher than that for two or more arms on a pump rotor. If this interference is to be avoided, either the rotative speed must be below the critical speed in which time is just allowed for the water to fall clear of the following arm or else the axis of the nozzle must be inclined at an angle to the path or plane of rotation. Since the preferred plane of rotation is horizontal, it follows that in such cases the axis of the nozzle will be directed downward or upward at such an angle as will insure freedom from interference. Any such depression or elevation of the axis of the nozzle for a given peripheral speed of the orifice and suction lift must inevitably increase the absolute velocity of discharge C2 and hence the efiiciency is somewhat lowered. On the other hand, by so doing a higher rotative speed is permitted.

The final solution in general will probably be some compromise between these conflicting requirements of high rotative speed and high efiiciency.

The angle of inclination, either in a downward or an upward direction is fixed by the dimensions of the pipe leading from the central chamber out to the nozzle insofar as it controls the size of the nozzle and by the pitch distance on the circle passing through the center of the nozzle. The shorter the pitch distance for a given size nozzle, the greater the angle of depression must be to avoid interference. The more nozzles there are, the shorter will be the pitch and hence the greater the depression. The greatest pitch distance and hence the minimum depression angle would occur in a pump with but a single arm and nozzle.

. For relatively smallcapacities an economical solution is to use a rotor with but one arm, as shown in Figures 3 and 4. The pump comprises the vessel having the central inlet chamber l 6 and the horizontally extending outlet arm l!, which latter is provided with the nozzle l8 having the discharge outlet or orifice l9 arranged to discharge the fluid, such as water, rearwardly in a direction of substantially 180 degrees to the peripheral speed vector of the orifice. This pump has the same proportions of elements, as above set forth, and. its orifice is located to position the vena contracta preferably in a radial plane. 20 is the counterweight provided to insure smooth running, this counterweight being opposed to the outlet arm and providing a balanced construction of pump. While this counterweight lies in the plane of the outlet arm, it terminates short of or inside the path of the jet of the fluid being discharged through the orifice l9.

In such a rotor, if the rotative speed is low encugh,the water may fall clear in the time of one revolution, even if there is no angle of jet inclination. As the rotative speed is increased,

rotative speeds it will be necessary to design the rotor as a high speed rotor and use some angle of jet inclination, even though there may be some sacrifice of eificiency.

.For greater capacities than can be conveniently obtained in a single arm rotor and/or to more nearly equalize the rotative balance, a pump having two arms of unequal length may be used. Such a pump is illustrated in Figures 5 and 6 in which the vessel has the central inlet chamber 2| and the long and short horizontally extending outlet arms 22 and 23 respectively. These arms lead from diametrically opposite sides of the inlet chamber and each arm is provided with the nozzle 24 having the discharge outlet or orifice 25 arranged to discharge the fiuid, such as water, in a direction opposite to the direction of rotation and located to preferably position the vena contracta in a radial plane. This pump also has the same proportions of elements as above set forth. The armswith their respective nozzles and discharge orifices have separate paths or planes of rotation and the path or plane of rotation of the long arm is above that of the short arm. Suitable means, such as the counterweight 26, is preferably provided for counterbalancing the pump. With this arrangement each nozzle and consequently the jet of the fluid, such as water, being discharged from the orifice of each nozzle has an individual path and all the advantages of the above the kinetic energy of the absolute velocity of discharge C. Expressed in terms of :head, rthis would be This velocity'head is energy which hasbeen put into the water by the rotor, hut whichcannot be readily utilized or converted into potential energy except by some means additionally provided.

It is therefore important that this velocity ;C be made as small as possible, if high efliciency is desired. In a low speed rotor, "that is one without jet inclination, the problem is relatively simple. All that is needed is .to employ a high peripheral speed relative to the suction lift. Thus, if a peripheral speed of feet per second is used for a suction lift of 10 feet, the resultant absolute velocity would be about 7.0 feet per second. This represents a head of 0.765 .feet or about 7.6% of the total head.

If the peripheral speed were 100 feet per second and the suction lift 10 feet, the resultant absolute velocity C would be about 3.0 feet per second. The velocity head is now 0.1g feet or 1.4% of the total head, etc. This calls for a relatively large diameter rotor and relatively low rotative speeds. The limit in this direction is larg one of cost. In order to avoid the high cost of a large'low R. P. M. rotor and casing, it is necessary to use higher rotative speeds, smaller diameter rotors, and finally jet inclination.

As soon as the axis of the jet is inclined, another problempresents itself. It now becomes necessary to limit the peripheral speed somewhat in order to secure the minimum value of C. In pumps without jet inclination, thehigher V, the smaller C would be for a given suction lift. This is not generally true for rotors having jet inclination. In such cases, it will be found that there is a certain value of peripheral speed for any given suction lift and angle of inclination which will give the minimum value of C. This can be found by drawing the vector diagrams for various values of V keeping the angle of inclination and suction lift constant. This makes it necessary to proportion the peripheral speed to suit either the angle of inclination or suction lift, or both, if satisfactory operating results are to be secured. For example, if the peripheral speed is too low for a given head the absolute velocity C will be not only too high but, worse still, the direction will be more nearly tangential than axial and the water splashes out of the casing and becomes difiicult to control. With this in mind in my invention, I do proportion the values of peripheral speed, suctionlift and angle of jet inclination so as to secure the best operating results. This can be expressed by the following limiting relations.

For any angle of jet inclination the diameter in feet of the rotor measured at the center of the discharge orifices should not exceed the value and should not be less than the value With a pump having a et depression. the v rtica distanc the water has to fall between the arms is from the ,upper level of the orifice area to the lowest level of the next following arm capable of causing interference in case there is .more than one arm, or to the lowest level of thesame arm capable of causing interference if there is 'but one. With a pump having a jet elevation the vertical distance the water has to rise between thearms isfrom the lower level of the orifice area tothe highest level of the next following arm capable of causing interference in case=there is .more than one arm, or to the highest level of the same armcapable of causing interference if there is but one. This axial distancemaybecalled S. There is quite a definite relation between the value of -S and the R. .P. M. of .the rotor and where S is theaxial distance in inches and N is the number pf arms capable of causing interference. The valueof S must be left below this value if interference is to be avoided when no angle of inclination is used.

,A number of methods for reducing the distance S and thereby increasing the .rotative speedof the pumpat whichinterferenceoccurs suggest themselves, .but regardless of the methodused, its value should be not greater than 900,000 (R. P. M. N)

unless there is some jet inclination.

In rotors having an angle of jet inclination a" (a. degrees) the angle of inclination is such that thesine a must be greater than S For all positive values of sine a where S is the-drop or rise in feet to clear the following arm, N is the number of the arms on the rotor in .thesame horizontal plane, Y is the peripheral speed expressed in feet of the-rotor at the centerlineof the. orifices and H is the total sue,- tion lift expressed in feet at'the junction of the arms.

'Theabove last mentioned equation'holds true for pumps having. eitherhorizontal or depressed jets, .but .with pumps having jetelevation the sine-11 shouldbeequal to or greater than Figures 7, 8, and 9=illustrate a pumpinwhich the axis of each nozzle is directed downward-at such-an angle as will insure freedom from interference of the fluid-being discharged with the following arm. The proportions of the elements of this pump, as set forth in all of the above formulae, are present. -In detail, the pump comprises the-vessel-having the central inlet chamber =2! and the horizontally extending outlet arms *28 radiating therefrom and together forming an S-shaped passage. The vessel also has thecentral depending annularflange 21 formingithe inlet.

zEachbf the. outlet anns,,as shown, is returnbentandihas atits outer end the. discharge outlet or orifice 29 which faces rearwardly relative to the direction of rotation of the vessel, so that the angle B is substantially 180 degrees. Each orifice is preferably located to position the center of the vena contracta in a radial plane. Each of the discharge orifices, as shown particularly in Figure 9, is positioned so that its axis is inclined, downwardly, so that the fluid being discharged therethrough may escape being struck by the following arm. 31! is a casing encircling the vessel and adapted to receive the fluid discharged therefrom. In order to regain a portion of the velocity head I have provided the curved deflector or guide 3| which is stationary and which extends beneath the vessel and flares upwardly and outwardly on expanding lines to a higher level, as determined by the height to which the fluid will flow as a result of its absolute velocity of discharge. In this way a portion of the absolute velocity C may be usefully regained in the form of potential energy and the efliciency of the pump improved. In cases where the amount of energy represented by the absolute velocity is negligible, the above mentioned guide or deflector may not be desirable as it increases the size and cost of the pump. In such cases, or when a certain amount of absolute velocity is desirable, as in liquid mixing or agitation, the bowl shaped guide or deflector may be omitted.

It will be noted that the vessel has the central depending annular flange 21 forming the inlet and the casing or receptacle has the upwardly and axially extending annular flange 39' telescopically engaging the annular flange 21' and that the height of the fluid discharged from the discharge orifices is such that it seals the joint between the annular flangesso that air cannot enter the inlet through this joint.

Figures 10 and 11 disclose another embodiment of my invention in which the pump has the same proportions of elements as previously set forth, but in which the distance S and consequently the angle a. are reduced. More in I detail, the vessel has the outer portions of its arms 32 reduced in diameter and provided at their free ends with the discharge outlets or orifices 33. These outer portions are in the nature of pipes which are curved rearwardly relative to the direction of rotation and which have external diameters but slightly greater than the diameters of the jets which it is desired to discharge. The discharge orifices may be formed by the open ends of the pipes or, if desired, by plugs in the ends of the pipes. With this arrangement, it will be seen that the distance S is greatly reduced and that the angle of inclination of the outer portions 32 of the arms, as shown more particularly in Figure 11, may be relatively small.

In order to utilize the advantages of higher rotative speed, some degree of inclination of the axis of the jet is generally necessary. This means that some amount of absolute discharge from the nozzle or discharge orifice is almost inevitable. This absolute velocity may be directed downwardly by depressing the angle of the axis of the jet, in which case the kinetic energy of the fluid may be lost unless additional means, such as shown in the modification illustrated in Figures 7, 8, and 9, are provided to recover some portion of this kinetic energy. If

the kinetic energy is small, it may be that no serious loss is incurred by discharging it directly into the pumped fluid casing or container. In this latter case, the cost of construction is about the minimum.

On the other hand, if higher efiioiencies are desired, the axis of the jet may be inclined upwardly and the resultant absolute velocity of discharge from the nozzle or the discharge orifice given a vertical component, whereby the fluid will rise above the plane of the discharge orifice and can be caught at a higher level. In this way much of the kinetic energy represented by the absolute velocity of discharge may be converted into potential energy and the efficiency of the pump thereby improved. The size and consequently the cost of the pump is generally increased by such a construction.

In some cases angles of jet inclination greater than that required to merely avoid interference may be used where higher absolute velocities of discharge are useful. For example, the fluid, such as water, might be pumped to a total head greater than the maximum suction lift, thereby extending the range of the pump.

, As illustrated in Figure 12, the pump has the same proportions of elements as previously set forth and it comprises the vessel 34 having the arms 35. The vessel is provided with the central fluid inlet 36 and the arms are each provided with the discharge outlet or orifice 31 and so arranged as to discharge the fluid, such as water, substantially rearwardly relative, but not exactly opposite, to the direction of rotation of the vessel. The axes of the discharge outlets or orifices are inclined upwardly to the path or plane of rotation of the centers of the outlets or orifices to an extent greater than that required to avoid interference by the arms and the fluid is discharged through the outlets or orifices upwardly and preferably outwardly with an absolute velocity such that this fluid may be caught by the receptacle 38, there being preferably the deflector 38' for assisting in directing the discharged liquid. This figure also shows a valve controlled outlet from this receptacle to the inner receptacle for containing the fluid to .seal the joint between the rotatable and stationary parts of the inlet connection.

The modification shown in Figure 13 also has the same proportions of elements as previously set forth, but in this modification the arms 39 are rotatably adjustably secured to the vessel 40 of the pump so that the axes of their discharge orifices or-outlets 4| may be inclined either upwardly or downwardly. The arrangement is such that the jet inclination may be varied as desired to secure proper and eflicient operation of the pump without interference with the discharged fluid at the speed at which the pump is to be driven.

Figure 14' shows another modification of pump also having the same proportions of elements as previously set forth. This pump has the vessel 42 from which extends the arms .43 rotatable in a gaseous medium, such as the atmosphere. Each of the arms has the discharge outlet or orifice 44, the axis of which is inclined downwardly so that the fluid, such as water, discharged has a vertically downward component. 45 is the casing or receptacle for the pumped fluid having the outlet pipe 46. This outlet pipe 46 extends above the bottom of the casing or receptacle, so that the height of the discharged fluid in the casing or receparms and extending across the casing or receptacle above its outlet pipe. This screen in operation permits the fluid discharged from the pump to pass downwardly into the lower portion of I the casing or receptacle, but prevents splashing of the fluid above the screen.

What I claim as my invention is:

l. A pump, comprising a rotatable inlet chamber and outlet arms extending from said inlet chamber, each of said outlet armsbeing provided with an outlet orifice rotating in a gaseous medium and so arranged as to discharge the fluid rearwardly relative to the direction of rotation of said outlet arms, one of said arms being shorter than the other and the axis of its outlet orifice being inclined at an angle to the path or plane of rotation of said arm, said shorter arm being positioned relative to said other arm in accordance with the angle of inclination.

2. A pump, comprising a rotatable inlet chamber and outlet arms extending from said inlet chamber, each of said outlet arms being provided with an outlet orifice rotating in a gaseous medium and so arranged as to discharge the fluid rearwardly relative to the direction of rotation of said outlet arms, one of said arms being shorter than the other and its path of rotation being below that of the other.

3. A pump, comprising a rotatable inlet chamber and outlet arms extending from said inlet chamber, each of said outlet arms being provided with an outlet orifice rotating in a gaseous medium and so arranged as to discharge the fluid rearwardly relative to the direction of rotation of said outlet arms, one of said arms being shorter than the other and its path of rotation being above that of the other, the axes of said outlet orifices being inclined upwardly at an angle to the path or plane of rotation of said arms.

4. A pump, comprising a rotatable vessel having a liquid inlet and a contracted liquid outlet having an appreciably less area than that of said inlet, said outlet rotating in air at substantially atmospheric pressure and having its axis inclined downwardly, the vena contracta of the liquid discharged from said outlet lying in substantially a radial plane, a receptacle for receiving the discharged liquid and a screen between said outlet and the'body of'liquid in said receptacle.

5, A pump, comprising a rotatable vessel having a fluid inlet and a contracted fluid, outlet having an appreciably less area than that of said inlet, said outlet rotating in air at substantially atmospheric pressure, the axis of said outlet being inclined upwardly and the vena contracta of the discharged fluid lying substantially in aradial plane, a receptacle and a deflector for guiding the discharged fluid to said receptacle.

6. A pump comprising a rotatable vessel having a fluid inlet and a contracted fluid outlet having an area appreciably less than the area of said inlet, said outlet rotating in air at substantially atmospheric pressure and being so arranged as to discharge the fluid rearwardly relative to the direction of rotation of said vessel with the center of the vena contracta in substantially a radial plane of said vessel, the axis of said outlet being inclined at an angle to the plane or path of rotation of its center.

'7. A centrifugal reaction pump comprising a central inlet chamber and outlet arms extending therefrom and rotating in air at substantially atmospheric pressure and provided with contracted outlets, whose aggregate area is appreciably less than the area of said inlet, said outlets being directed to discharge the fluid substantially rearwardly relative to the direction of rotation of said vessel, the vena contracta lying in substantially a radial plane and said outlet arms being adjustable whereby the axes of said outlets may be inclined at any desired angle to the plane or path of rotation of said outlet arms.

8. A pump comprising a rotatable vessel havinga fluid inlet and arms curved opposite tothe' direction of rotation of said vessel provided with contracted fluid outlets at their ends, said outlets having an aggregate area appreciably less than the inlet area and lying in substantially radial planes, the axes of said outlets being inclined to the plane of rotation of said outlet arms and said outlets rotating in air at atmospheric pressure, and a stationary upwardly and outwardly flared guide arranged to convertpart of the kinetic energy of the fluid discharged from said outlets into potential energy.

9. A pump. comprising a rotatable vessel having a fluid inlet and a contracted fluid outlet, said outlet being appreciably less in area than that of said inlet, said outlet lying in a substantially radial plane and so arranged as to discharge the fluid substantially opposite to the direction of rotation. of said vessel, said outlet rotating in air at substantially atmospheric pressure, the axis of said outlet being inclined downwardly to the plane of rotation of said vessel and a stationary upwardly. and outwardly extending flared guide arranged to receive the fluid discharged from said outlet and to convert part of the absolute velocity of the discharged fluid into potential energy. 7

1.0. A liquid pump comprising a rotatable vessel having a liquid inlet and a contracted liquid outlet, the area of said outlet being appreciably less than that of said inlet, said outlet being directed substantially opposite to the direction of rotation of said vessel and the axis of said outlet being inclined to the plane of rotation of said vessel and said outlet rotating in air at substantially atmospheric pressure, and a stationary guide for re ceiving the liquid discharged from said outlet, said guide being curved upwardly andoutwardly and compelling the discharged liquid to rise in annular form to a point above said outlet by reason of the absolute velocity.

11. Apump comprising a rotatable vessel having a fluid inlet and a contracted fluid outlet orifice having an area appreciably less than that of said inlet, said outlet orifice substantially lying in aradial plane and rotating in air at substantially atmospheric pressure, the axis of said outlet orifice being inclinedto the plane of rotation of said vessel.

12. A pump comprising a rotatable vessel having a central depending annular flange providingflo an inlet and arms rotating in air at substantially atmospheric pressure provided with contracted outlets at their ends, said outlets being appreciably less in aggregate area than the area of said inlet and said outlets lying in substantially radial planes, the axes of said outlets being inclined at an angle to the plane of rotation of said vessel and arms, and a receptacle for the pumped liquid having an axially extending annular flange telescopically engaging said first mentioned annular flange and also having means for maintaining the liquid at a level in said receptacle to seal the joint between said annular flanges.

13. A pump comprising a rotatable vessel having a fluid inlet and a contracted fluid outlet having substantially less area than that of said inlet, said outlet rotating in and discharging into a gaseous medium at a pressure substantially that acting on the fluid being pumped, the axis of said outlet being inclined at an angle to the plane of rotation of said outlet and said outlet substantially lying in a radial plane, and the direction of the relative velocity of flow through 1 said outlet being substantially opposite to the direction of rotation of said outlet.

ALLEN F. SHERZER. 

